Gearing arrangement of mangling or wringing machines



May 24, 1932 E. LoucHE-r 1,860,041

GEARING ARRANGEMENT OF MANGLING 0R WRINGNG MACHINES Filed July 50, 1928'7 Sheets-Sheet l May 24, 1932. 1,860,041

GEARING ARRANGEMENT oF MANGLING oa WRINGING MACHINES E. LQUCHET FiledJuly 30. 1928 '7 Sheets-Sheet 2 May 24, W32. E. LoUcHET SM i GEARINGARRANGEMENT OF MANGLING OR WRINGING MACHINES Filed July 30. 1928 7Sheets-Sheet 3 Fig. 5

`Q3 n lg z 27 wwf/wf?1 May 24, 1932. A E. LoUcHET 1,860,041

GEARING ARRANGEMENT OF MANG'LING OR WRINGING MACHINES 7 Sheets-Sheet 4Filed July 50. 1928 May 24, 1932. E. LouHET I 1,860,041

GEARING ARRANGEMENT OF MANGLING' OR WRINGING' MACHINES Filed July 50.1928 7 Sheets-Sheet 5 Fig AT TUR/VE Y May 24, 1932. E. LoUcHET 1,860,041

GEARING ARRANGEMENT 0F MANGLING OR WRINGING MACHINES Filed July 30. 1928'7 Sheets-Sheet 6 gm. H

A TURA/EY E. LOUCHET GEARING ARRANGEMENT OF MANGLING OR WRINGINGMACHINES May 24, 193,2. l

Filed July so. 1928 '7 Sheets-Sheet 7 nlv 3.

Patented May 24, 1932 Unirse lSTATES PATENT rclerics a EDMOND LOUGHET,orv ROUBAIX, FRANCE, AssIGNon. 'or' ONE-nary To socr'r ATELIERS ST.ELOI, OF TOURCOING, FIRAIWCI'] GEARING ARRANGEMENTOF MANGLINe-onwnrneine livrAcrLInnsf Application med July 3o, 192s, serial N0.-asasez, and in rranequly 29,1927,

The pressesused in the Vwashing of wool and: other textile matters showlserious inconvenlences from the viewpoint of the spar-u ing of thematter to be squeezed as well as onaccount of the fact that the mode ofdriv-` ing of said upper roller through long-toothed gearing betweenboth the upper and lower rollers causes speed of said upper roller everytime a new tooth passes along; and

Second. A difference in the speeds o f the rollers, resulting from theupper roller being driven by long-toothed gearing and at the Y whichmust exist between both rollers if an effective squeezing effect is tob-e obtained. In order to reduce in av certain proportion suchdisagreement, the long-toothed gear of the upper roller is not,generally, keyed' on the shaft vof said roller, but is 'driven by meansof a pawl or trigger, a ratchet-wheel being integral with the shaft ofthe upper roller which can, at giventimes and on acat an angularspeedgreater than that which would result from a long-toothed gear drive.W'hen such device comes into action (which it can do in onedirection'only), then the driving of the upper roller takes `placethrough' the point of contact,'which is detrimental to the material tobe squeezed,said material undergoing a frictional strain which isgreater inasmuch as the motion of the upper roller is different fromthat which is transmitted bythe long-toothed gears.

My invention has for its object a device by which said inconveniencesare vobviated, the long-toothed gears being dispensed with and thedriving of the upper roller being obv. main drive and eachl` roller.First. An instantaneous variation 1n the ments. y Y

Figures l and2 show, in front and side Vlews respectively,one o f theseembodiments,

siderable on account of the great pressure count of the slope of theratchet teeth, travel tained through an intermediatemember, the

axis of .which is positioned, as far as possible,

on a line substantially level with the center p of the upper roller inthe non-operative position of thelatter.- Y ;Thisintermediate member bywhich my invention is characterized in its chief object may beinterposed inthe driving mechanism either between both rollers-orbetween the It may consist, for instance, of a worm spindle and wheel,bevel or spur gears or any other known means, such means being,infaddition, combined so thatthe movement of rotation of the upperroller may be made wholly or substantially independent vof the lift'offsaid roller in the ordinary limits ofK practice.

The drawingsappended hereto show, for mere indicative purposes, somepossible embodiments of my above mentioned improve- Figurel being partlyin section.

. Figs. 3 and 4 and Figs. 5 and 6 are, respectively, views similar toFigs.k l and 2 and show modifications of the invention.l

' Fig. vis a view similar to and illustrating l said shaft 39 drives,through gear 41, the shaft 8 of the lower roller 9 of the press. 0n`

the same shaft 39 are mounted sleeves44 and 45 on which gears 46 and 47are free to rotate.

On `the other hand, the finely toothed gear 48 iskeyed at the end ofshaft 39. `This gearV i drives, through a Vsuitably mounted idle gear49, the removable or detachable gear `14. The

latter rotates shaft-50-on which it is 5 keyed and which bears heavilytoothed pinions 60 and 61. Thesev two pinions drive, Vthrough thel,abovev mentioned loose gears 46 and 47 gears 53 and 54 fixed toshaft54 of the upper roller of the press.

` As gears 46 and 47 mesh with gears54 and 53 on asubstantially'horizontal,line it follows that the upper roller of thepress is able, together with its shaft 54', torise'an appreciabledistance without any likelihood of the gears 46 and 447 becomingdisengaged from gears 54 and 53. The mechanical drive of the upperYroller is thus ensured, whatever thickness the layer of wool interposedbetween-rollers 2 and 9 may be, much more effectively than by ordinarylong-toothed gears, a constant ratio being vat the same time maintainedbetween the driving and the driven parts. By having th-e center of gear46 just below the level of shaft 54 when the upper roller 2 hasundergone no wear yet, such upper roller may be allowed to wear aconsiderable amount without loosing the'beneiit of this regular drive.,t Y

The removable ordetachable gear 14 at the end of shaft may easily bereplaced. Its number of teeth determines the speed ratio of rollers 2and 9 of the press.

'Ihe intermediate gear member 49 borne by a stub shaft on a.semi-circular plate`49"rotat able on shaft 39 and secured by means ofslots and 56 and nuts 57 and 58 takes care of the driving (Figure 2).The changes inthe angular speed of the roller are obtained by theprovision of limited weight andeasily fitted gears of which it is notexpensive to have a set in stock. .Practically it is suflicient Vto havea set of gears which differ in their numbers'of teeth by twosuccessively. WithV a seven gear set it is possible'to obtainthetheoretical speeds for the upper roller notwithstanding a wear amountingto 14 centimeters on the diameter of such roller.

As gears 46 and 47 apply on upper roller 2 an upward stress proportionalto the resistance of the press -to operation it follows that, by suchdriving arrangement, the press takes Vupthe material under treatmentmost easily Y and that there is much less liability fortlie wool to packor accumulate in advance of the rollers. Y

Whatever the position of the upper roller may be in the limits ofpractice, 'the speed of the latter as results from being driven by y theintermediate members remains 'always over-thickness.

position of elevation of the former.

constant but, considering the moment when said upper roller rises ordescends, the speed is not absolutely constant. v

As regards the pressure between both rollers, it diminishes when roller2 has to y rise on account of a thicker Vsheet being fed,

the Cardan joint is driven by bevel pinion 26 and a bevel gear 27, thelatter being keyed on shaft 2S of the gear box. Y Figures 5 and 6 showthat both worm wheel and wormmay be rreplaced by two bevel gears 29 and30. Gear 30 is driven by key 21 iixed on shaft 19". The latter is drivenby means of spur gears 31 and 32, bevel pinion 26, bevel gear 27 and thegear box 7".

In the two above mentioned cases (Figures 3 and 4, 5 and' 6) an angularyspeed of the upper roller 2a or 2b, completely independent of the liftof said roller, is obtained. f

In the paticular case of Figure 7, a worm V13b is fixed in position bybeing keyed on its vertical driving shaft. Suchv arrangementv gives anapproximate solution, inasmuch as every vertical displacement of theupper roller 2b causes a slight variationin its movement of rotation,said acting, then, .as a rack Vwith respect to the worm wheel 17 b.

In the cases of Figures 3v and 4 (movable worm) and Figures 5 and 6(movable bevel gear), the pressure between the two rollers is entirelyindependent of the upwardA or downward movement of the upper roller 2a.or 2b; the vertical stress between the worm 18 and` Worm wheel 17, andbetween the bevel gears 29 and 430, being cancelled by the reaction ofthe casing 20 fixed to the said upper roller. n

In the' arrangement of Figure 7 (fixed worm), the pressure between thetwo rollers diminishes when the upper roller 2b is about to rise; sothat here again there is a reduction ofthe likelihood of failure ofthepress to operate through kclogging of the rollers. In allthe abovementioned embodiments the number of the exchangeable pinion, or theposition at which the handle ofthe gear box must be set may, forinstance, be indicated by means of a pointer 36 moved across an indexeddialv 37 by means of a rod 38 connected to the shaft ofthe upper rollers2, 2a and 2b. It need not be mentioned that, instead of being positionedbetween the upper and lower rollers, the intermediate members lmay beinterposed between the upper roller and the main drive shaft 39 of thepress or between each of the rollers and said shaft 39. Inasmuch as thenumber of revolutions of the latter, for instance in the presses ofwashing machines, is generally tenfold that of the lower roller which itdrives through pinions 40 and 41, it is easier to use smallsized pinionsas intermediate members.

Having now particularly ascertained and described the nature of my saidinvention as well as the manner in which the same is to be performed, Ideclare that what I claim is:

In a press for squeezing textile or other materials, upper and lowerpressing rollers between which the materiall is fed by the pressure ofthe rollers, means for applying power to the lower roller, intermediarygear trains imparting rotary motion to the upper roller substantiallyindependently of lift of that roller due to passage of a portion of thematerial of abnormal thickness between the rollers, the gear elements ofsaid intermediary gear trains transmitting power to the upper rollerbeing located in a plane substantially horizontal with the axis of theupperrollerga main drive shaft, and a con nection between the same andthe lower roller, the rotation of the upper roller being effected bysaid shaft through the intermediary gear trains; an auxiliary shaftwhereon the gears Y ofthe intermediary gear trains which impart rotarymotion to the upper roller are mounted for rotation independently ofeach other; a pinion fixed for rotation with saidv auxiliaryshaft; aplate mounted for angular adjustment at one side of the press; meanswhich impart rotary motion to the upper f.

roller, thereby to permit the upper roller to rise a reasonable distancewithout separation of the meshing gears.

In testimony whereof I aiiix my signature.

EDMOND LOUCHET.

